Hydraulic and electric control device

ABSTRACT

A hydraulic and electric control device for selectively opening and closing a hydraulic valve includes an actuating device for energizing an electric motor which drives a pump to send liquid through the valve. The control device is provided with a lost motion connection between the valve and the valve actuating device so that the electric motor will not be energized to operate the pump until the valve is in its maximum open position.

United States Patent [72] Inventors John K. Tomko 2,397,736 4/1946 Hadekel 137/565 X Euclid; 2,568,052 9/1951 Catranis 251/294 X William W. King, Cleveland Heights, both 3,195,574 7/1965 Carls 251/78 X of, Ohio 3,515,167 6/1970 Svenson 137/565 1 1 l 3 1 222 FOREIGN PATENTS [22] He 191288 1 Patented Sept. 1971 l/1907 Germany 137/565 [73 Assignee Meyer Products, Inc. Primary Examiner-M. Cary Nelson Cleveland, Ohio Assistant ExaminerR. B. Rothman AttorneyMeyer, Tilberry & Body [54] HYDRAULIC AND ELECTRIC CONTROL DEVICE 9 Claims, 14 Drawing Figs.

52] us. c1 137/565,

, 74/ 102, ZOO/61.86 ABSTRACT: A hydraulic and electric control device for [51] Int. Cl FlSb 15/18 selectively opening and closing a hydraulic valve includes an [50] Field of Search 137/565; actuating device for energizing an electric motor which drives 251/78, 294, 242, 243; 261/27; ZOO/61.86; 74/102 a pump to send liquid through the valve. The control device is provided with a lost motion connection between the valve and Refuemes C'ted the valve actuating device so that the electric motor will not UNITED STATES PATENTS be energized to operate the pump until the valve is in its max- 974,774 11/1910 c3111 261/27 imum P P i 28 T a 1 f I {28 a PATENTEB SEP] 4 l97i SHEET 2 [IF 7 INVENTORS JOHN K. ram/(0 BY WILL/AM w. mm

W film my ATTOR/VEXS PATENTEU SEPI 419m sum 3 0F 7 INVENTORS JOHN K. TOM/(0 WILL/AM M4 /(/N6 A TTORNEYS PATENTED SEPMISYI 3.8043454 sum u UF 7 E 62 0 66 2 //5 82 9g 4 96 62 lm 9 //0\ 51.366 0090 OQIQ 9 [/2 o soooc as //a 78 80 INVENTORS JOHN K. TOM/(O BY WILL/AM M. K/NG ATTORNEYS PATENTED SEP] 4197! SHEET 5 OF 7 INVENTORS JOHN K. TOM/(0 WILL/AM M. KING ATTORNEYS 'PATENTED SEP] 4 I971 sum 7 OF 7 INVENTORS JOH/V K. mu/(0 BY WILL/AM m mm ATTORNEYS HYDRAULIC AND ELECTRIC CONTROL DEVICE BACKGROUND OF THE INVENTION This application pertains to the art of hydraulic and electric control devices and more particularly to a control device for selectively opening and closing a hydraulic valve, and for energizing an electric motor to operate a pump which sends liquid through the valve. The invention is particularly applicable for use with vehicle mounted snowplows whose angularity and raised position relative to the vehicle may be adjusted by hydraulic cylinders. However, it will be appreciated that the invention has broader applications and can be used in other environments utilizing hydraulic cylinders for adjustment pur poses.

In prior hydraulic and electric control devices, a manual adjustment was provided to insure complete opening of a valve before an electric motor was energized to drive a pump which sent liquid through the valve. Such manual adjustments were often difficult to make and improper adjustment would cause energization of the motor prior to complete opening of the valve. In addition, operation of such prior devices often caused the manual adjusting device toloosen or wear and cause premature energization of the motor before the valve was completely opened.

SUMMARY OF THE INVENTION In accordance with the present invention, a hydraulic and electric control device is provided with an improved arrangement which insures complete opening of a valve before an electric motor is energized to drive a pump which sends liquid through the valve. More specifically, the control device of the present invention includes a hydraulic valve actuator and an electric switch actuator. The valve actuator includes a lost motion means which is operative subsequent to movement of the valve to a fully opened position to allow movement of the electric switch actuator to a switch energizing position. With the control device of he present invention, the electric switch actuator cannot be moved to a switch energized position until the valve is in its completely opened position. I

It is a principal object of the present invention to provide a hydraulic and electric control device which insures complete opening of a hydraulic valve before an electric motor is energized to drive a pump which sends liquid through the valve.

It is another object of the present invention to provide such a control device which is very simple to manufacture and assemble, and is very reliable in operation.

BRIEF DESCRIPTION'OF THE DRAWING The invention may take-physical form in certain parts and arrangements of parts, a preferred embodiment of which will be described in detail in this specification and illustrated in the accompanying drawings which form a part hereof.

FIG. 1 is a side, elevational view of a hydraulic and electric control device constructed in accordance with the present invention;

FIG. 2 is a top plan view looking in the direction of arrows 2--2 of FIG. 1;

FIG. 3 is a partial cross-sectional view looking in the direction of arrows 3-3 of FIG. '1;

FIG. 4 is a partial cross-sectional view looking in the direction of arrows 44 of FIG. 1;

FIG. 5 is a cross-sectional view looking in the direction of arrows 5-5 ofFIG. 2;

FIG. 6 is a cross-sectional view looking in the direction of arrows 6-6 of FIG. 1;

FIG. 7 is a view similar to FIG. 6 and showing the control device of the present invention in an intermediate operated position;

FIG. 8 is a partial plan view showing the control device of the present invention in an intermediate operated position;

FIG. 9 is a view similar to FIG. 6'and showing the control device of the present invention in afully actuated position;

FIG. l0v is a view similar to FIG. 8 and showing the control device of the present invention in a fully operated position;

FIG. 11 is a diagrammatic illustration showing one valve arrangement for use with the actuator of FIG. 1;

FIG. 12 is a diagrammatic illustration similar to FIG. 11 an DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings, wherein the showings are for purposes of illustrating the preferred embodiment of the invention only and notfor purposes of limiting same, FIG. 1 shows a hydraulic and electric control device constructed in accordance with the present invention. The control device includes a substantially U-shaped support A having spacedapart substantially vertical end walls 10 and I2, and a substantially horizontal bottom wall 14. Bottom wall 14 may have a plurality of holes 16 therein through which screws or bolts may be passed to secure support A to a suitable surface such as the framework inside the engine compartment of a motor vehicle.

In accordance with the invention, a second substantially U- shaped support member B, which is substantially smaller than support member A, is positioned on bottom wall 14 intermediate end walls 10 and 12 of support member A. Support member B includes spaced-apart substantially vertical end walls l8 and 20, and a bottom wall 22. Walls 18 and 20 of support'B are substantiallyparallel to one another, and to end walls 10 and 12 of support A. Bottom wall 22 of support member B may be secured to bottom wall 14 of support member A as by spot welding or by any other suitable means such as screws or bolts. End wall 12 of support member A is provided with a pair of spaced-apart circular holes 24 and 26 through which end portions of cylindrical rods C and D slidably extend. A pair of levers, on the upper ends of which suitable handgrips or knobs may be secured, include lower bifurcated portions defining spaced-apart leg members 32 and 34, and 36 and 38. Rods C and D, and legs 32-38, are provided with suitable holes through which pins 42 and 44 extend forpivotally connecting the bifurcated portions of levers 28 and 30 with rods C and D. Wall 20 of U-shaped support memberB is provided with a pair of spaced-apart ears, only one of which is shown at 46 in FIG. 1. Ear 46 and a link 48 are provided with suitable holes through which pin 50 extends for pivotally connecting link 48 with ear 46. Link 48, and legs 32 and 34 of lever 28, arezprovided with suitable holes through which a pin 52 extends. A similar link 54 is provided for connection to' legs 36 and 38 of lever 30 by pin 56. With this arrangement, it will be recognized that a pushing or pulling movement on lever 28 to the shadow line positions shown in FIG. 1 will cause rod C to move axially to the left or to the right as viewed in FIG. 1.

In accordance with the preferred arrangement, the forward end portions of rods C and D are provided with cylindrical enlargementsE and F. Slidably received over each of cylindrical enlargements E and F are a pair of substantially cylindrical sleeve members 58. Sleeve members 58 include a radially extending circumferential flange 60 at one end thereof. Sleeve members 58 are retained on cylindrical enlargements E and F as by C-rings 62 received in circumferential grooves 64 formed in the exterior surface of cylindrical enlargements E and F. A coil spring 66 is received on each of enlargements E and F between sleeve members 58 to normally bias sleeve members 58 away from one another and into engagement with C-rings62. Each end wall 18 and 20 of support member B is provided with a pair of spaced-apart holes or U-shaped slots 68 and 70, and 72 and 74, respectively. Sleeve members 58 are received in U-shaped slots 68-74 with flanges 60 positioned between the inner facing surfaces of end walls 18 and 20. Flanges 60 bear against the inner surfaces of walls 18 and 20 adjacent slots 68-74.

In accordance with the invention, cylindrical enlargement E of rod C is provided with a small diameter cylindrical recess 76 and a larger diameter recess 78 which intersect at a circumferential shoulder 80. While the arrangement will be described only with reference to cylindrical enlargement E of rod C, it should be understood that the arrangement shown in FIG. 6 is identical to that for enlargement F of rod D. Slidably received within large cylindrical recess 78 are a pair of ferrule members 82 and 84. Ferrules 82 and 84 are retained within large cylindrical recess 78 as by a C-ring 86 received in a circumferential groove 88 fonned in the wall of recess 78. Ferrules 82 and 84 include facing end portions 90 and 92. A rod member G includes a small diameter cylindrical portion 94 received through suitable holes in ferrules 82 and 84. One end portion of small diameter rod portion 94 is exteriorly threaded for receiving a nut 96 which bears against radially inward extending flange 98 of ferrule 84. Rod member G includes a larger diameter cylindrical portion 102 which intersects small diameter portion 94 at a circumferential shoulder 104. Shoulder 104 bears against radially inward extending flange 106 on ferrule 82. Rod member G includes a further enlarged end portion 108 having a substantially axial cylindrical recess 110 therein for receiving a bowden wire 112. A threaded radial cylindrical recess 1 14 in end portion 108 intersects axial recess 1 and a set screw 116 threaded into threaded recess 114 has its end portion bearing against bowden wire 112 to retain bowden wire I12 securely in axial recess 110. A coil spring 118 positioned around small diameter rod portion 94 of rod member G biases against flanges 98 and 106 of ferrules 82 and 84 to normally bias ferrules 82 and 84 away from one another and into engagement with C-ring 86 and shoulder 80. Facing end portions 90 and 92 of ferrules 82 and 84 are normally spaced apart from one another as shown in FIG. 6.

With the arrangement described, it will be recognized that coil spring 66 normally acts to place rods C and D in a static neutral position with levers 28 and 30 in a substantially vertical neutral position as shown with respect to lever 28 in FIG. 1.

Adjacent end wall 12 of support member A, a support bracket I-I, having a pair of end flanges 122 and 124, and a raised support portion 126, is secured to bottom wall 14 as by spot welding flanges 122 and 124 thereto. Raised support portion 126 is provided with threaded holes 130 through which screws 132 are threaded after extending through suitable holes in conventional miniature switches 134 and 136. Switches 134 and 136 are normally open and are provided with reciprocating actuators 138 and 140. When secured to support portion 126, miniature switches 134 and 136 are positioned between rod members C and D with actuator 138 facing rod C and actuator 140 facing rod D. Each rod C and D is provided with a small diameter portion 142 and 144 having oppositely sloping cam surfaces 146 and 148, and 150 and 152 at the respective end portions thereof. With rods C and D biased to their normal static position by coil springs 66, reduced diameter portions 142 and 144 of rods C and D are normally located directly opposite actuators 138 and 140 of switches 134 and 136 as shown in FIG. 2.

In the preferred arrangement, coil spring 118, which biases ferrules 82 and 84 apart, is considerably stronger than coil spring 66 which biases sleeve members 58 apart. In one arrangement, coil spring 118 is around double the strength of coil spring 66 with spring 118 being a 40-pound spring and with coil spring 66 being a -pound spring. With this arrange ment, a pushing movement of lever 28 toward the left-hand shadow line position as viewed in FIG. 1 will cause rod member C to move axially to the left as viewed in FIG. 1. This movement will cause coil spring 66 to be compressed and flange 60 on right-hand sleeve 58 will move away from the inner face of end wall 20 as shown in FIG. 7. At the same time, cylindrical enlargement E will slide relative to the left-hand sleeve member 58 which cannot move axially to the left as viewed in FIG. 7 because flange 60 bears against the inner face of end wall 18. This movement of rod member C axially to the left as viewed in FIGS. 1 and 7 will also cause rod member G to move axially to the left. When moved to an intermediate position, with end wall 20 positioned intermediate flange 60 on right side sleeve 58 and right side C-ring 62, small diameter portion 142 of rod C will move relative to actuator 138 of switch 134 to a position shown in FIG. 8. In this position, switch 134 will still be open. In the position of FIG. 7, the device with which bowden wire 112 is connected is incapable of further movement. Therefore, continued pushing movement on lever 28 to the left-hand shadow line position shown in FIG. 1 makes it impossible for rod member G to move further axially to the left as viewed in FIG. 7 because bowden wire 112 cannot move. Under such condition, spring 118 will begin to compress and shoulder will act against flange 98 of ferrule 84 to move end 92 of ferrule 84 toward end of ferrule 82 which cannot move due to contact to flange 106 with shoulder 104 on rod member G which likewise cannot move. Cylindrical enlargement E will then move axially to the left as viewed in FIG. 7 relative to rod member G until the parts reach the position shown in FIG. 9. As shown in FIG. 9, righthand C-ring 62 will be in contact with the outer face of end wall 20 while the outer surface of flange 98 on ferrule 84 is spaced from nut 96 and end portions 90 and 92 of ferrules 82 and 84 are in contact with one another. In addition, during movement from the position of FIG. 7 to the position of FIG. 9, small diameter portion 142 of rod C will have shifted relative to actuator 138 of switch 134 to the position shown in FIG. 10. During this movement, cam portion 148 will act against actuator 138 to close switch 134. Release of pushing force on lever 28 will automatically cause all of the parts to return to the positions of FIGS. 1, 2 and 6 through action of springs 66 and 1 18.

It will be readily apparent that a pulling movement of lever 28 toward the right-hand shadow line position of FIG. 1 will cause a similar lost motion movement between the parts. A pulling movement axially to the right on rod C as viewed in FIG. 6 will cause flange 60 of left-hand sleeve 58 to move away from the inner face of end wall 18. In an intermediate position of movement, end wall 18 will be positioned intermediate left-hand C-ring 62 and flange 60 of left-hand sleeve 58. In such position, rod member G will have moved axially to the right along with rod C due to the more powerful force exerted by spring 1 18 as compared with spring 66. In such intermediate position of movement, the device to which bowden wire 112 is connected will not be capable of further movement. Therefore, further pulling movement of lever 28 will cause coil spring 118 to compress as C-ring 86 exerts a force axially toward the right in FIG. 6 on flange 106 of ferrule 82. Flange 106 will then move axially to the right away from shoulder 104, which cannot move because rod member G cannot move, and ends 90 and 92 of ferrules 82 and 84 will be positioned closely adjacent or in contact with one another. During this further movement from the intermediate position described, cam portion 146 of rod C will have moved actuator 138 of switch 134 inward to close switch 134.

In accordance with the invention, end wall 10 of support A is provided with a pair of spaced-apart holes 158 and 160. As shown in FIG. 5, a bowden cable J, which includes a straight wire 112 positioned for axially sliding movement relative to a spiral wire sheath 162, has a connecting member 164 with internal threads 166 threaded onto its end portion. Connecting member 164 includes a tubular exteriorly threaded portion 168 extending through holes 158 and a nut 170 threads onto tubular portion 168 for retaining sheath 162 of bowden cable J against movement relative to end wall 10. Another bowden cable Y is secured to end wall 10 by connector 174 and nut 176 in the same manner as described with reference to FIG. 5. Bowden cable Y includes bowden wire 172 connected to rod member G of rod D.

Bowden cable J, which is operated by rod C and lever 28, extends from support A to connection with a valve K in FIG. 11. Wire 112 of bowden cable J may be received in an axial recess formed in end portion 182 of valve actuator L and retained in position by a setscrew 184 threaded into a radial slot in end portion 182. Valve actuator L includes enlarged end portions 186 and 188, and a central enlarged portion 190. A reduced diameter portion 192 separates portions 186 and 190, and a reduced diameter portion 194 separates portions 188 and 190. Large diameter portions 186-190 are cylindrical and are adapted for axial sliding movement in bore 198 formed in valve K. Suitable seals may be provided in a wellknown manner to prevent leakage. Valve K includes secondary drainage ports 202 and 204 communicating with bore 198 and with a main drainage port 206 leading to reservoir 208 for hydraulic fluid. Valve K includes an inlet port 210 communicating with bore 198 and with reservoir 208 through hydraulic pump 212. Conduit 214 extends from reservoir 208 to pump 212, and conduit 216 extends from pump 212 in inlet port 210. Valve K further includes outlet ports 220 and 222. Outlet port 220 communicates with the forward end of hydraulic cylinder M through conduit 224 and with the rear end of hydraulic cylinder N through conduit 226. Outlet port 222 communicates with the forward end of hydraulic cylinder N through conduit 228 and with the rear end of hydraulic cylinder M through conduit 230. Hydraulic cylinder M includes a piston 232 and a rod 234, while hydraulic cylinder N includes a piston 236 and a rod 238. Hydraulic cylinders M and N are preferrably secured to the framework of a motor vehicle with rods 234 and 238 pivotally connected with suitable brackets 7A0 and 242 as at pivots 244 and 246 of snowplow moldboard P. A suitable bracket 248 on moldboard P is provided for pivotally connecting the moldboard P to the frame of the motor vehicle as at pivot point 250. Valve actuator L of valve K is provided with circumferential grooves receiving C-rings 252 and 254 for limiting axial movement of valve actuator L relative to valve K. A suitable electric motor 256 is drivingly connected with pump 212 for selectively operating pump 212 to send hydraulic liquid through valve K when motor 256 is energized.

Bowden cable Y, which is operated by rod D and lever 30, extends from support A to connection with a hydraulic valve R. Wire 172 of bowden cable Y is received in a suitable axial recess in end portion 260 of valve actuator S and retained in position by setscrew 262 threaded into a suitable radial recess formed in end portion 260. Valve R includes a discharge port 264 communicating with reservoir 208 through conduit 266. Valve actuator S includes large diameter cylindrical end portions 268 and 270 axially slidable in cylindrical bore 272 of valve R, and intermediate small diameter portion 273. Valve R includes an inlet port 274 communicating with bore 272 and with conduit 216 on the discharge side of pump 212 through conduit 276. Valve R also has an outlet port 278 communicating with the rear end of a hydraulic cylinder T through conduit 280. Hydraulic cylinder T includes a piston 282 and rod 284 which pivotally connected to a link 286 as at 288. Hydraulic cylinder T is also pivotally connected to the framework of a motor vehicle U as at pivot 290. Link 286 is pivotally connected to the framework of motor vehicle U as at 292 and with a chain 294 at pivot point 296. Chain 294 is pivotally connected with links 298 and 302 as at pivot point 304. Link 302 is pivotally connected with the framework of motor vehicle U as at 305 and with moldboard P as at 306. Link 298 is pivotally connected with moldboard P as at 308.

In operation of the device, levers 28 and 30 are in their intermediate vertical position with the parts positioned as shown in FIGS. 1, 2 and 6. The parts are normally biased to this intermediate static position by springs 66 and 118 as previously described. Pushing movement on lever 28 toward the lefthand shadow line position of FIG. 1 transmits a pushing force force through wire 1 12 of bowden cable .I to valve actuator L of valve K. Valve actuator L then shifts axially to the right and to the position shown in FIG. 12. With valve actuator L positioned as shown in FIG. 12, C-ring 252 is bearing against the end portion of valve K so that valve actuator L can move no further axially to the right. In this position, secondary discharge port 202 is completely blocked by large diameter end portion 186 while secondary discharge port 204 is completely open and unobstructed by large diameter end portion 188 and is in communication with bore 198. In addition, inlet port 210 is completely open and unobstructed by intermediate large diameter portion 190. Outlet ports 220 and 222 are also completely open and unobstructed by large diameter end portions 186 and 188. In this position of valve actuator L of valve K, valve K is in a first, completely open position and the lost motion device is positioned as shown in FIG. 7. In this position, end wall 20 of support B is positioned intermediate right-hand C-ring 62 and flange 60 of right-hand sleeve member 58 as shown in FIG. 7. Also, reduced diameter portion 142 of rod C is in an intermediate shifted position relative to actuator 138 of switch 134 as shown in FIG. 8. Therefore, motor 256 is not energized and pump 212 is not operating so that no liquid is being pumped through valve K. Further pushing movement on lever 28 permits no further movement of rod member G because C-ring 252 on valve actuator L is bottomed against the end portion of valve K and wire 112 of bowden cable cannot move axially. Under these conditions, further pushing movement on lever 28 will cause rod C and enlarged diameter portion E to move axially relative to rod member G and spring 118 will be compressed so that ferrule 84 moves toward ferrule 82. In the left-hand shadow line position of lever 28 as shown in FIG. 1, the parts will be arranged as shown in FIGS. 9 and 10, with right-hand C-ring 62 on enlarged diameter portion E bearing against the outer face of end wall 20 of support B. In addition, small diameter portion 142 of rod C will have moved to the position shown in FIG. 10 and actuator 138 of switch 134 will have been cammed inwardly by cam portion 148 to close switch 134. Motor 256 is then energized to operate pump 212 which draws hydraulic liquid from reservoir 208 through conduit 214 and sends liquid through conduit 216 to inlet port 210 of valve K. This fluid will then flow through outlet port 220 to the forward end of hydraulic cylinder M through conduit 224 and to the rear end of hydraulic cylinder N through conduit 226. This will cause piston 232 of hydraulic cylinder M to move rearwardly while piston 236 of hydraulic cylinder N will move forwardly. At the same time, port 222 is completely open as is secondary discharge port 204 so that hydraulic liquid may drain from the rear end of hydraulic cylinder M and the forward end of hydraulic cylinder N through conduits 228 and 230. This hydraulic fluid drains through port 222, bore 198, secondary discharge port 204 and main discharge port 206 back to reservoir 208. With this manner of operation, moldboard P will be pivoted counterclockwise as viewed in FIGS. 11 and 12. Releasing pushing force on lever 28 will cause it to return automatically to its full line intermediate vertical position as shown in FIG. 1 due to the action of springs 66 and 118. Valve actuator L will then return to its closed position as shown in FIG. 11 so that discharge ports 202 and 204 are blocked by.

large diameter portions 186 and 188, and inlet port 210 is blocked by intermediate large diameter portion 190. In this condition, hydraulic fluid cannot enter or leave hydraulic cylinders M and N so that moldboard P will be retained in any desirable clockwise shifted position.

It will be understood that a pushing force on lever 30 will operate valve actuator S of valve R in a similar manner. Pushing movement on lever 30 transmits pushing force through wire 172 of bowden cable Y to valve actuator S. This causes valve actuator S to shift axially to the right as viewed in FIG. 1 1 to the position shown in FIG. 12. In this position, inlet port 274 is closed by large diameter portion 268 while discharge port 264 and outlet port 278 are completely open and unobstructed by large diameter end portion 270. In this position, hydraulic fluid may drain from the rear end of hydraulic cylinder T through conduit 280, port 278, bore 272, port 264 and conduit 266 back to reservoir 208. The weight of moldboard P acting on piston 282 accomplishes drainage from cylinder T. In addition, rod D is provided with a circumferential groove receiving a C-ring 312 to hold a sleeve member 313 on rod D as shown in FIG. 2. While rod C has a similar circumferential groove 315, no C-ring is provided in groove 315 of rod C. C-ring 312 and sleeve 313 are provided on rod D to prevent energization of motor 256 during pushing movement of lever 30 for rod D. In addition, circumferential groove 64 in the right-hand end portion of cylindrical enlargement F, as viewed in FIG. 2, is closer to the small diameter portion of rod D than is the corresponding circumferential groove in cylindrical enlargement E. Therefore, C-ring 62 is spaced from the end of right-hand sleeve member 58 on cylindrical enlargement F around one-sixteenth of an inch as shown in FIG. 2. With sleeve member 313 bearing against C- ring 312, sleeve member 313 is also spaced around one-sixteenth inch from the outer surface of end wall 12. Therefore, a pushing movement on lever 30 will shift rod D axially to the left as viewed in FIG. 2. This leftward movement allows cylindrical enlargement F to freely move axially relative to sleeve members 58 and coil spring 66 surrounding cylindrical enlargement F. Due to the spacing of right-hand C-ring 62 on cylindrical enlargements F, pushing movement on lever 30 opens valve R to drain hydraulic cylinder T without any corresponding movement of associated parts as described with FIGS. 6, 7 and 9. In addition, sleeve member 313 will strike against the outer surface of end wall 12 before switch 136 is actuated by cam surface 152. Due to the spaced positioning of right-hand C-ring 62 on cylindrical enlargement F, axial movement of rod D to the left as viewed in FIG. 2 takes place only against frictional resistance and not against any springbiasing force. Therefore, the frictional resistance will maintain rod D in a shifted position with valve R open to drain hydraulic cylinder T so that moldboard P has a floating action. A positive pulling force on lever 30 is then required to move rod D back to its neutral position in which spool S of valve R is again closed as shown in FIG. 11.

With the parts positioned as shown in FIGS. 1, 2, 6 and 11, a pulling movement on lever 28 toward the right-hand shadow line position shown in FIG. 1 will cause valve actuator L of valve K to move to the position shown in FIG. 13. In this position, end wall 18 of support B will be positioned intermediate left-hand C-ring 62 and flange 60 of left-hand sleeve member 58. With end wall 18 positioned in this intermediate position, C-ring 254 will bear against the end portion of valve K so that valve actuator L cannot move any further axially to the left. In this position, secondary discharge port 202 is completely open and unobstructed by large diameter end portion 186 while secondary discharge port 204 is completely closed by large diameter end portion 188. Also in this position, ports 210, 220 and 222 are completely open and unobstructed. With enlarged diameter portion E of rod C moved axially to the right as viewed in FIGS. 2 and 7 so that end wall 18 of support B is intermediate left-hand C-ring 62 and flange 60 of left-hand sleeve 58, C-ring 254 on valve actuator L will bear against the end portion of valve K so that valve actuator L cannot move any further axially to the left as viewed in FIG. 13. With end wall 18 of support B in such intermediate position, further pulling force on lever 28 will not permit further movement of rod member G because wire 112 of bowden cable .1 cannot move axially any further. Therefore, further pulling movement on lever 28 to the right-hand shadow line position shown in FIG. 1 will cause C-ring 86 to bear against flange 106 of ferrule 82 so that ferrule 82 moves to the right as viewed in FIG. 6 until end portions 90 and 92 are closely adjacent one another or abutting. In the maximum right-hand position of lever 28 as viewed in FIG. I, left-hand C-ring 62 of FIG. 6 will bear against the outer surface of end wall 18 on support B. With such further movement, cam portion 146 of rod C will operate switch actuator 138 to close switch 134 to energize motor 256 which drives pump P to draw liquid from reservoir 208 through conduit 214 and cause liquid to flow through conduit 216 to inlet 210 of valve K. Liquid will then flow through bore 198 and outlet port 222. Liquid then flows from port 22 through conduit 228 to the forward end of hydraulic cylinder N and through conduit 230 to the rear end of hydraulic cylinder M. This will cause piston 232 to move forward and piston 236 to move rearward. Hydraulic fluid will drain from the forward end of cylinder M through conduit 224 and from the rear end of cylinder N through conduit 226 to port 220. Fluid will then flow through port 220, through bore 198, through secondary discharge port 202 and main discharge port 206 back to reservoir 208. This provides clockwise movement of moldboard P about pivot point 250 as viewed in FIG. 13. When the pulling force on lever 28 is removed, lever 28 will automatically return to its full line intermediate position as shown in FIG. 1 due to the action of springs 66 and 118. Release of the pulling force will also cause the springs to reposition valve actuator L in its closed position as shown in FIG. 11. This will once again cause large diameter portions 186, 188 and 190 to block secondary discharge ports 202 and 204, and inlet port 210, so that fluid cannot escape from cylinders M and N, and moldboard P will be held in its desired adjusted clockwise pivoted position. i

A pulling movement on lever 30 will likewise shift rod D in the same manner as described with reference to pulling movement of lever 28 for rod C. This pulling movement of lever 30 will transmit pulling force through wire 172 of bowden cable Y and shift valve actuator S of valve R axially to the left and to the position shown in FIG. 13. In the position shown in FIG. 13, C-ring 314, which is received in a circumferential groove in end portion 270 of valve actuator S, will bear against the right-hand end of valve R so that valve actuator S can move no further axially to the left. In this position, end wall 18 of support B will also be intermediate left-hand C-ring 62 and flange 60 of left-hand sleeve member 58 on rod D. Likewise in this position, small diameter portion 144 of rod D will have shifted axially relative to actuator of switch 136 but will not have moved a sufficient distance for cam portion to operate actuator 140. Further pulling force on lever 30 of rod D does not permit further movement of rod member G because bowden wire 172 cannot move axially due to C-ring 314 being bottomed against the end of valve R. Therefore, enlarged diameter portion F of rod D will move axially to the right relative to rod member G against the force of spring 118 due to C-ring 86 bearing against flange 106 of ferrule 82. During this further shifting movement of rod D, cam portion 150 will act against switch actuator 140 to close switch 136 and energize motor 256 to drive pump 212. Pump 212 will then draw hydraulic liquid from reservoir 208 through conduit 214 and send such liquid through conduit 276 to inlet port 274 of valve R. Liquid will then flow unobstructed through inlet port 274 through bore 272 and outlet port 278 to the rear portion of hydraulic cylinder T through conduit 280. This will cause piston 282 of hydraulic cylinder T to move upwardly for raising or angling moldboard P relative to vehicle U. Releasing the pulling force on lever 30 will cause rod D to automatically assume its intermediate neutral position due to the action of springs 66 and 118, and this automatic action will also move valve actuator S axially to the right and back to the position shown in FIG. 11. In the axial shifted position as shown in FIG. 13, it will be recognized that end portion 270 completely blocks discharge port 264 so that fluid sent through valve R by pump 212 flows only to hydraulic cylinder T.

FIG. 14 shows one diagrammatic arrangement for connecting motor 256 to a storage battery W positioned in a motor vehicle. Switches 134 and 136 are positioned in parallel so that operation of either switch will close the circuit from battery W to motor 256 to energize motor 256 and drive pump 212. It will be recognized that switches 134 and 136 may be connected to actuate solenoid switches which connect battery W with motor 256 so that the full current flowing to motor 256 will pass through the solenoid switches and not through switches 134 and 136.

In devices of the character described, the vehicle U often has lights, a radio, heater and other accessories. Therefore, it

is extremely important to conserve the energy of battery W when operating motor 256 to adjust the position of moldboard P. In previous arrangements, it was possible to have premature energization of motor 256 before either of valves K or R were in a completely open position. Under such conditions, motor 256 would have to run much longer so that pump 212 could supply sufficient fluid to move moldboard P to a desired adjusted position because either the inlet or outlet ports of the valves would be partially blocked. In accordance with the present invention, it is not possible to energize motor 256 until the valves are in a completely open position with the inlet and outlet ports being completely open and unobstructed. This conserves considerable energy of battery W and prevents excess drainage of electricity by excessive operation of motor 256.

It will be recognized that valves K and R are selectively movable between the closed position of FIG. 11 and an open position of FIG. 13. These two open and closed positions may be termed first and second positions of valves K and R. In addition, levers 28 and 30, along with rods C and D and their enlarged diameter portions E and F, cooperate with the parts described with reference to FIG. 6, and with bowden cables J and Y to define valve-actuating means. Both of levers 28 and 30 are movable to the right from the full line position shown with reference to lever 28 in FIG. 1, to a position intermediate the right-hand shadow line position in which wall 18 of support B is positioned intermediate left-hand C-ring 62 and flange 60 of left-hand sleeve member 58. Movement between such positions may be termed third and fourth positions of movement for levers 28 and 30 and the actuating means defined. It will also be recognized that the defined valve-actuating means includes the small diameter portions and cam portions of rods C and D which define operating means for closing switches 134 and 136 to actuate pump 212. In addition, the structure defined with reference to FIGS. 6, 7 and 9 defines lost motion means which is operative subsequent to movement of either of the levers to one of the third or fourth positions to free the valve-actuating means for movement past such position to a pump starting position in which either of switches 134 or 136 are closed to energize motor 256. It will also be recognized that the force required to shift valve actuators L or S axially is less than the force of spring 118 so that rod member G will not shift relative to tubular portions E and F of rods C and D during actuating movement of rods C and D. With reference to valve K, it will be recognized that FIG. 11 illustrates an intermediate position of valve actuator L while FIGS. 12 and 13 illustrate different shifted positions of valve actuator L. Therefore, the full line position of lever 28 shown in FIG. 1 may be termed an intermediate position of the control device while partial shifted positions of lever 28 intermediate the rightand left-hand shadow line positions shown may be termed third and fourth positions corresponding to the positions of valve actuator L as shown in FIGS. 12 and 13. With this arrangement, springs 66 and 118 define biasing means which normally biases the actuating means back to the intermediate full line position shown in FIG. 1 for lever 28 when pushing or pulling force is removed from lever 28. It will be recognized that spool L of valve K may itself be spring biased to the intermediate closed position as viewed in FIG. 11. Spring biasing of spool L will assist springs 66 and 118 in returning spool L to the neutral position shown in FIG. 11 when pushing or pulling force is removed from lever 28. In addition, it is also possible to have spool S of valve R spring biased for return to the position of FIG. 11 when moved to the position of FIG. 13. Such spring biasing would not come into action during movement of spool S between positions of FIGS. 11 and 12 so that floating action of moldboard P may be accomplished as previously described. It will also be recognized that the diagrammatic description of valves K AND R is merely illustrative and it is also possible to use a single four-way valve for operating the hydraulic cylinders. It is also possible to utilize single-acting hydraulic cylinders rather than doubleacting cylinders as diagrammatically illustrated and described.

It will also be recognized that levers 28 and 30 may be directly actuated by a person grasping a suitable handgrip secured thereto or by connecting bowden cables or other suitable linear actuators to levers 28 and 30 so that operation of the bowden cables from the cab of a vehicle would operate the control device positioned within the engine compartment of a vehicle.

While the invention has been described'with reference to a preferred embodiment it is obvious that modifications and alterations will occur to others upon the reading and understanding of this specification.

Having thus described our invention, we claim:

1. A control device for operating hydraulic valve means and pump means, said control device including selectively movable valve-actuating means for connection with said valve means to selectively move said valve means between first and second positions when said actuating means is selectively moved between third and fourth positions, said control device including movable pump-actuating means for selectively starting and stopping operation of said pump means to supply hydraulic fluid past said valve means, said valve-actuating means including operating means for moving said pump-actuating means to a pump-starting position, said valve actuating means including lost motion means operative subsequent to movement of said valve-actuating means to at least one of said third and fourth positions to free said valve-actuating means for movement past said one position to a pump-starting position, said operating means moving said pump-actuating means to a pump starting position during movement of said valve-actuating means to said pump-starting position from said one position.

2. The device of claim 1 wherein said pump-actuating means comprises electrical switch means for selectively energizing electric motor means to drive said pump means, said lost motion means comprising resilient yieldable means interposed between said valve means and said valve-actuating means, said yieldable means having a predetermined stiffness sufficient to remain substantially unyielding during movement of said valve means between said first and second positions by operation of said valve-actuating means between said third and fourth positions, said yieldable means yielding under greater force applied to said valve-actuating means at said one position to free said valve-actuating means for movement beyond said one position to said pump-starting position in which said operating means closes said electrical switch means.

3. The device of claim 1 wherein said valve-actuating means includes an intermediate actuating position between said third and fourth positions corresponding to an intermediate position of said valve means, and biasing means normally biasing said actuating means to said intermediate position and automatically returning said actuating means to said intermediate position from said third or fourth positions or said pump-starting position.

4. The device of claim 1 wherein said valve-actuating means includes axially reciprocatable rod means, support means supporting said rod means for axial reciprocating movement, said rod means being movable between said third and fourth positions and said pump starting position, said rod means having an intermediate position between said third and fourth positions, abutment means on said rod means, and spring means acting between said support means and said abutment means and normally biasing said rod means to said intermediate position, said spring means automatically returning said rod means to said intermediate position from said third or fourth positions or said pump-starting position.

5. The device of claim 4 wherein said pump-actuating means comprises electrical switch means for energizing electric motor means to drive said pump means and said operating means comprises cam means on said rod means, said cam means cooperating with said switch means to close said switch means when said rod means moves beyond said one position to said pump-starting position.

. another and defining said lost motion means, and biasing spring means acting between said shaft means and said tubular portion and normally biasing said shaft means and said tubular portion to a predetermined axial position relative to one another, said rod means and said tubular portion being axially shiftable relative to said shaft means against biasing force of said biasing spring means during movement of said rod means to said pump-starting position from said one position.

7. The device of claim 1 wherein said lost motion means is operative subsequent to movement of said valve-actuating means to either of said third or fourth positions to free said valve-actuating means for movement past either said third or fourth positions to a pump-starting position, said operating means moving said pump-actuating means to a pump-starting position during movement of said actuating means to said pump-starting position from either of said third or fourth posi tions.

8. The device of claim 7 wherein said valve-actuating means includes an intermediate actuating position between said third and fourth positions corresponding to an intermediate position of said valve means, and biasing means normally biasing said actuating means to said intermediate position and automatically returning said actuating means to said intermediate position from said third or fourth positions or said pump-starting position.

9. The device of claim 8 wherein said pump-actuating means comprises electrical switch means for selectively energizing electric motor means to drive said pump means, said lost motion means comprising resilient yieldable means interposed between said valve means and said valve-actuating means, said yieldable means having a predetermined stiffness sufficient to remain substantially unyielding during movement of said valve means between said first and second positions by operation of said valve-actuating means between said third and fourth positions, said yieldable means yielding under greater force applied to said valve-actuating means at either of said third or fourth positions to free said valve-actuating means for movement beyond either said third or fourth positions to said pump-starting position in which said operating means closes said electrical switch means. 1 

1. A control device for operating hydraulic valve means and pump means, said control device including selectively movable valveactuating means for connection with said valve means to selectively move said valve means between first and second positions when said actuating means is selectively moved between third and fourth positions, said control device including movable pump-actuating means for selectively starting and stopping operation of said pump means to supply hydraulic fluid past said valve means, said valve-actuating means including operating means for moving said pump-actuating means to a pump-starting position, said valve actuating means including lost motion means operative subsequent to movement of said valve-actuating means to at least one of said third and fourth positions to free said valveactuating means for movement past said one position to a pumpstarting position, said operating means moving said pumpactuating means to a pump starting position during movement of said valve-actuating means to said pump-starting position from said one position.
 2. The device of claim 1 wherein said pump-actuating means comprises electrical switch means for selectively energizing electric motor means to drive said pump means, said lost motion means comprising resilient yieldable means interposed between said valve means and said valve-actuating means, said yieldable means having a predetermined stiffness sufficient to remain substantially unyielding during movement of said valve means between said first and second positions by operation of said valve-actuating means between said third and fourth positions, said yieldable means yielding under greater force applied to said valve-actuating means at said one position to free said valve-actuating means for movement beyond said one position to said pump-starting position in which said operating means closes said electrical switch means.
 3. The device of claim 1 wherein said valve-actuating means includes an intermediate actuating position between said third and fourth positions corresponding to an intermediate position of said valve means, and biasing means normally biasing said actuating means to said intermediate position and automatically returning said actuating means to said intermediate position from said third or fourth positions or said pump-starting position.
 4. The device of claim 1 wherein said valve-actuating means includes axially reciprocatable rod means, support means supporting said rod means for axial reciprocating movement, said rod means being movable between said third and fourth positions and said pump starting position, said rod means having an intermediate position between said third and fourth positions, abutment means on said rod means, and spring means acting between said support means and said abutment means and normally biasing said rod means to said intermediate position, said spring means automatically returning said rod means to said intermediate position from said third or fourth positions or said pump-starting position.
 5. The device of claim 4 wherein said pump-actuating means comprises electrical switch means for energizing electric motor means to drive said pump means and said operating means comprises cam means on said rod means, said cam means cooperating with said switch means to close said switch means when said rod means moves beyond said one position to said pump-starting position.
 6. The device of claIm 4 wherein said rod means includes a tubular portion and said valve-actuating means includes shaft means received in said tubular portion, said shaft means and said tubular portion being axially reciprocable relative to one another and defining said lost motion means, and biasing spring means acting between said shaft means and said tubular portion and normally biasing said shaft means and said tubular portion to a predetermined axial position relative to one another, said rod means and said tubular portion being axially shiftable relative to said shaft means against biasing force of said biasing spring means during movement of said rod means to said pump-starting position from said one position.
 7. The device of claim 1 wherein said lost motion means is operative subsequent to movement of said valve-actuating means to either of said third or fourth positions to free said valve-actuating means for movement past either said third or fourth positions to a pump-starting position, said operating means moving said pump-actuating means to a pump-starting position during movement of said actuating means to said pump-starting position from either of said third or fourth positions.
 8. The device of claim 7 wherein said valve-actuating means includes an intermediate actuating position between said third and fourth positions corresponding to an intermediate position of said valve means, and biasing means normally biasing said actuating means to said intermediate position and automatically returning said actuating means to said intermediate position from said third or fourth positions or said pump-starting position.
 9. The device of claim 8 wherein said pump-actuating means comprises electrical switch means for selectively energizing electric motor means to drive said pump means, said lost motion means comprising resilient yieldable means interposed between said valve means and said valve-actuating means, said yieldable means having a predetermined stiffness sufficient to remain substantially unyielding during movement of said valve means between said first and second positions by operation of said valve-actuating means between said third and fourth positions, said yieldable means yielding under greater force applied to said valve-actuating means at either of said third or fourth positions to free said valve-actuating means for movement beyond either said third or fourth positions to said pump-starting position in which said operating means closes said electrical switch means. 